CN100429431C - Power transmission mechanism with linear and rotation movement conversion - Google Patents

Power transmission mechanism with linear and rotation movement conversion Download PDF

Info

Publication number
CN100429431C
CN100429431C CNB2004100845199A CN200410084519A CN100429431C CN 100429431 C CN100429431 C CN 100429431C CN B2004100845199 A CNB2004100845199 A CN B2004100845199A CN 200410084519 A CN200410084519 A CN 200410084519A CN 100429431 C CN100429431 C CN 100429431C
Authority
CN
China
Prior art keywords
cam
cylinder
power transmission
transmission mechanism
inner chamber
Prior art date
Application number
CNB2004100845199A
Other languages
Chinese (zh)
Other versions
CN1779297A (en
Inventor
赵荃
Original Assignee
赵荃
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 赵荃 filed Critical 赵荃
Priority to CNB2004100845199A priority Critical patent/CN100429431C/en
Publication of CN1779297A publication Critical patent/CN1779297A/en
Application granted granted Critical
Publication of CN100429431C publication Critical patent/CN100429431C/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01BMACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H25/00Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/08Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
    • F16H25/12Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal, or cams
    • F16H25/125Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal, or cams having the cam on an end surface of the rotating element

Abstract

The present invention relates to a power transmission mechanism of a space cam for switching linear movement and rotary movement. The present invention aims to provide a power transmission mechanism of a cam of an inner cavity channel that the movement rules of linear movement components can be artificially designed; a guide hole (a cylinder hole) 2 does not undertake the support function. The present invention is characterized in that rolling wheels are arranged near the outer ends of a roller shaft 16 on the upper part of a cam 6 of an inner cavity channel in a cam box 15, and are arranged on the contour of circumferential cams of the cam 6 of an inner cavity channel. The roller shaft 16 is also provided with a guide roller or a slide block 27. The lower end of a cam box cover body 1 is axially arranged in a fixed guide rail 4. The present invention can serve as prime movers of gasoline, diesel oil and gas internal combustion engines, Stirling external combustion engines, gas and liquid motors, etc., power transmission mechanisms of pumps for transporting gas and liquid, or other fields with the requirement of movement conversion.

Description

Straight line motion and the power transmission mechanism that rotatablely moves and change

Technical field

The present invention relates to straight line motion and rotating movement converting device, specifically relate to the rotatablely move mechanism of conversion of parallel to-and-fro motion of roller shaft and inner chamber groove cam, more specifically say to relate to reciprocating motion of the pistons and the inner chamber groove cam power transmission mechanism that rotatablely moves.

Background technique

On December 28th, 1994, the invention disclosed number of patent application was 94100421.x " cam-type piston internal-combustion engine ", disclose two kinds and be referred to as to comprise the three-dimensional cam ring of formula, be enclosed in the cylinder body outside, can be " single piston is lighted mechanism " (not having embodiment not have accompanying drawing in the specification), also can be the two combustion of double-piston mechanism, as Fig. 1, Fig. 4, Fig. 5 ".Its force-bearing situation of the power transmission mechanism of above-mentioned disclosed " cam-type piston internal-combustion engine " and " Cam Design of automatic " Peng Guoxun, Xiao Zhengyang work, the 9th page, Fig. 1-5, a) cylindrical cam mechanism is similar, and it is identical with the 174th page of non-cantilever shape of Fig. 5-7 cylindrical cam mechanism free-body diagram a (the two combustion of foregoing invention double-piston mechanism map 1, Fig. 4, Fig. 5), figure b cantilever shape (foregoing invention claims single piston to light mechanism) to be research object with piston (follower lever).The 173rd page " non-cantilever shape follower lever cylindrical cam mechanism is under load Q effect, because the relative axis tilt of counter-force P (a+ μ 1), will produce frictional force respectively at guided bearing A and C place.”。Find out that easily the bearing pin of foregoing invention Fig. 4, Fig. 5 is the overhang that an end freely supports in three-dimensional convex race, fulcrum is at bearing pin axle end bearing place, be balance, another fulcrum is at the piston upside, if piston is not installed, described bearing pin and bearing just can not normally carry out straight reciprocating motion; In addition,, when satisfying the lift of piston, just must increase the cam diameter if use double peak to valley, this moment the piston axes line to the fulcrum pin axle axle end bearing apart from extending, just increase piston countercylinder wall lateral force, influence piston, cylinder working life.Owing to use unimodal single paddy cam, can only bearing be set at bearing pin one end, load all acts on this bearing, influences working life.When piston from a stop work done return, during the work done of the other end piston, because of downward projection of last peripheral cam profile and following peripheral cam profile overlapping fully, the side of bearing pin bearing in peripheral cam profile groove crossed and impacted opposite side, roller will produce the torque opposite sign this moment, cause heavy wear near crossing a little.Obviously, it also is very difficult being fit into the bearing pin axle end bearing in the above-mentioned three-dimensional convex race or changing its bearing, and inconvenience is safeguarded.In addition, can not close, obtain the internal-combustion engine of different capacity, the seriation difficulty by above (as four cylinders, six cylinders, eight cylinders) the cylinder array of simple two cylinders; Cylinder head and part distribution device will redesign test fully, and inheritance is poor, the cost height.

Connecting rod has the history in more than 100 year as interior alkene acc power transfer mechanism, has become perfect now, and has become conventional engine.Deficiency is: 1, worst connnecting rod big end swing is a vibratory source uneven and that can't eliminate in its three kinds of forms of motion; 2, can not realize reciprocating motion of the pistons four times or six times, eight times, bent axle only revolves and turns around; 3, piston is gone up the stop curve and can not be realized isochoric combustion; 4, expansion space stroke piston motion acceleration limit the boundary line of power, promptly limited the internal-combustion engine high-power; 5, the active force of piston head change into the branch line of force that connecting rod promotes crankshaft rotating and crank spindle directly the distance of shaft center line be variable, making the piston movement speed curve is sinusoidal curve, it or not curve of equal velocity, therefore crankshaft torque is not a straight line just also, the speed of expansion of high-temperature fuel gas is restricted, and the thermal efficiency is low; 6, because of piston imposes on cylinder wall to the side direction active force in the High Temperature High Pressure rugged environment, can not lubricate by working pressure, frictional loss is big, and mechanical efficiency is low; 7, cylinder is being born the function of supporting, so piston must have bigger skirt section; 8, the piston skirt piston-pin boss is near piston head, and circumferential thickness is irregular, must make face oval structure, processed complex for preventing the thermal expansion locking; 9, piston both pumped in cylinder, and alternately swinging again relies on casing wall, and piston ring groove just produces relative fricting movement with piston ring, so piston ring groove and piston ring end face are easy to wear; 10, increase equilibrium block and accumulated energy flywheel must be set because of the off-centre of crank throw produces dynamic and static imbalance, increase engine weight; Though 11, its main shaft diameter and impose reaction to topple over the piston of power be the motion lower pair all is a circular arc camber, obviously can not improve mechanical efficiency and be restricted with pressure lubrication oil supporting spindle footpath and piston; 12, the also all only suitable at every turn cylinder igniting work done of multicylinder engine, rate is hanged down in the cylinder utilization.

Existing employed rhombus driving mechanism, connecting rod, swash plate or pendulum disk mechanism, four connecting rod swing-block mechamisms all can not really be accomplished the piston discontinuous fluid of Stirling cylic engine requirement, do not have lateral forces simultaneously in cylinder wall.

High pulling torque reciprocating piston type gas, hydraulic motor, the connecting rod of use, swash plate or pendulum disk mechanism, torque wire is not a straight line, can not realize identical moment of torsion output.

Summary of the invention

1. the object of the invention is: provide several roller shafts to be the inner chamber groove cam power transmission mechanism of the non-cantilever beam structure of two ends free end bearing at least on inner chamber groove cam peripheral cam profile.

2. the object of the invention is: several piston (directly moving bar), cylinders (pilot hole) of not being provided with are provided, still can realize the power transmission mechanism that parallel linear reciprocating motion of roller shaft and inner chamber groove cam rotatablely move and change.

3. the object of the invention is: provide several supporting forces of toppling over of inner chamber groove cam transmission that make to act on away from the inner chamber groove cam power transmission mechanism on the fixed guide of cylinder.

4. the object of the invention is: provide several pistons not have lateral forces in cylinder wall, allow cylinder only have sealing, guide function, do not bear the inner chamber groove cam power transmission mechanism of supporting functions.

5. the object of the invention is: the active force of several piston head is provided, and changing the effect branch line of force that promotes rotating motion part into is definite value to the distance of shaft center line, realizes the inner chamber groove cam power transmission mechanism of identical moment of torsion output easily.

6. the object of the invention is: provide several characteristic needs according to all kinds motor, but the people is an inner chamber groove cam power transmission mechanism of designing required desirable piston motion curve (as above with or the discontinuous fluid, the movement at the uniform velocity that stop down, come and go different Motion curves etc.).

7. the object of the invention is: provide several total loads of piston head that allow be shared by at least two rollers, thereby alleviate the inner chamber groove cam power transmission mechanism of every main roller bearing load.

8. the object of the invention is: several rollers in the space groove cam are provided, and no matter under various working staties, the sense of rotation of roller all remains unchanged, and promptly roller does not produce the inner chamber groove cam power transmission mechanism of torque opposite sign.

9. the object of the invention is: several rollers that make nearly each outer end of roller shaft are provided, in the as easy as rolling off a log inner chamber geosynclinal convex race of packing into, just simultaneously also the utmost point safeguard the inner chamber groove cam power transmission mechanism of (as tear open old, more renew roller).

10. the object of the invention is: provide several and need only close (as two cylinders, four cylinders, six cylinders, eight cylinders, ten cylinders etc.) by simple cylinder array, just can obtain the inner chamber groove cam internal-combustion engine of different capacity.

For achieving the above object, the invention provides a kind of straight line motion and the power transmission mechanism that rotatablely moves and change, comprising: the inner chamber groove cam can be formed with continuous cam path around its axis rotation on its cylindrical cavity wall; Support and hold the cam box of inner chamber groove cam, have the lid that is positioned at the cam box top, and the fixed guide that is installed in the inner chamber that extends into the inner chamber groove cam under the lid; Realize the assembly of straight reciprocating motion, comprise that the axis perpendicular to the inner chamber groove cam is provided with roller shaft, respectively at the adjacent installation in roller shaft two end part and main roller that in described cam path, moves and auxilliary roller, be arranged on the described roller shaft and along the guiding element of guide rail movement, described roller shaft forms the non-cantilever beam structure that two ends are at least freely supported described in the inner chamber groove cam, wherein, the motion of described roller shaft is simultaneously synthetic along moving of fixed guide by main roller and motion and the guiding element of auxilliary roller in cam path.

Technological scheme: the straight line motion and the transfer power transfer mechanism that rotatablely moves.Comprise pure rotational motion spare: the inner chamber groove cam; Straight reciprocating motion assembly: roller shaft, guide roller or slide block 27, main roller 9 and auxilliary roller 37; Fixed block supporting mass: cam supporting mass (cam box) 15, lid (cylinder body) 1, fixed guide 4.Inner chamber groove cam 6 is housed in cam box 15, and the lid 1 on its top is fixed on sealing cam box 15 on the cam box 15; There is nearly each outer end of a roller shaft that main roller 9 and auxilliary roller 37 all are housed in the cam box 15, on inner chamber groove cam 6 groove inner circumference cam profiles, rolls; The fixed guide 4 relative positions that axially are provided with in roller shaft and lid 1 lower end also are provided with guide roller or slide block 27, but scroll-up/down or slip in fixed guide 4, Fig. 1.

Inner chamber groove cam power transmission mechanism.Comprise pure rotational motion spare exportable, input power: the inner chamber groove cam; Straight reciprocating motion assembly: roller shaft, guide roller or slide block 27, main roller 9 and auxilliary roller 37, piston 5, piston rod 5a; The fixed block supporting mass: cylinder cap 28 is provided with the cylinder body (lid) 1 in cylinder hole (pilot hole) 2, fixed guide 4, cam box 15; The inner chamber groove cam is housed in cam box 15, and its top is provided with the cylinder body 1 that cylinder cap 28 is housed and has cylinder hole 2 and is fixed on the cam box 15; The piston rod 5a bottoms that fix with piston 5 in the cylinder hole 2 are contained on the cam box 15 interior roller shafts, in nearly each outer end of roller shaft main roller 9 are housed and auxilliary roller 37 rolls on inner chamber geosynclinal convex race inner circumference cam profile; The position that the fixed guide that axially is provided with in the axis of rolling and cylinder body 1 lower end 4 is relative also is provided with guide roller or slide block 27 in fixed guide 4, Fig. 1 a.

Inner chamber geosynclinal convexization of the present invention is an end is the output supported end, and the other end has round cavity, its inner chamber circumference be provided with identical fluctuating, the double peak to valley groove being used to lead at least, and go up peripheral cam profile 7 and have at least two breach 12.Identical three peaks, three paddy are arranged, and last peripheral cam profile 7 has inner chamber groove cam 6a such as Fig. 2 b of three breach 12; Or there are identical four peaks, four paddy, last peripheral cam profile 7 to have inner chamber groove cam 6b Fig. 2 a of two or four breach 12; Or five identical peak five cereals are arranged, last peripheral cam profile 7 has the inner chamber groove cam of five breach 12 etc.

Inner chamber groove cam of the present invention, can by a peripheral cam profile have identical, at least double peak to valley end cam 46 (subordinate's peripheral cam profile 8), peripheral cam profile 46 corresponding with end cam with one also have identical, double peak to valley and inward flange cam 3 (peripheral cam profile 7 on the genus) with at least two breach 12 fix and combine at least, as Fig. 2 a, 2b; Described inward flange 3 can use mould, makes its shaping with power.

Inner chamber groove cam of the present invention is a steel part, use casting or cold machining process manufacturing, comprise, following peripheral cam profile has relative motion surface at interior each, carburizing or carbonitriding is carried out in the temperature of carburizing or carbonitriding at least one place or many places, the size number of austenite crystal that makes surface layer is greater than 10, it is enough thin to mean that austenite crystal has, with this crackle that stops the decortication by internal start to cause, prolong tired working life, carrying out surface hardening again in 790-830 degree centigrade temperature of the said temperature that is lower than carburizing or carbonitriding handles, on, the working surface of following peripheral cam profile can produce and be at least the residual stress under compression and have a rupture stress that is at least 2650Mpa of baroclining of 500Mpa, with further life-saving

For ease of changing roller, inner chamber geosynclinal convex race inboard has at least two holes that communicate with the outside 22, and as Fig. 2 a, or described breach 12 extends to down peripheral cam profile 8 places by last peripheral cam profile 7, as Fig. 1, Fig. 2 b, Fig. 4; Above-mentioned breach 12 all is arranged on lower dead center (stop down) and locates, and as Fig. 4 a, 4b, or all is arranged on top dead center (go up and stop) and locates, and as Fig. 4 c, it is wide identical with roller diameter at least, Fig. 4.

Inner chamber groove cam of the present invention on it axially downward projection of peripheral cam profile 7 working curved surfaces not overlapping or not exclusively overlapping with following peripheral cam profile 8 working curved surfaces; The upper and lower peripheral cam profile of inner chamber groove cam of the present invention can be intilted go up peripheral cam profile 7 and or peripheral cam profile 8 down, as Fig. 9.

Piston 5 usefulness bolts 23 of the present invention are fixed on the piston rod 5a, as Fig. 6.Piston rod 5a is single pin or multiway structure such as Fig. 6 a to Fig. 6 b.The lower end surface of end in contact has the loop wire 79 of protrusion on described bolt 23 and the piston 2, and the height of protrusion is guaranteed the sealing of 5 in bolt 23 and piston in 1mm, Fig. 6, Fig. 6 e.

There are single cylinder and the coaxial setting of inner chamber groove cam in cylinder hole (pilot hole) 2 on the cylinder body of the present invention (lid) 1, or is provided with at one or two circumferences 50,51 and the one kind of intersection of bisector to five bisectrix.Fig. 7 a is a circumference 50 and 67 liang of crosspoint places of bisector two cylinder holes 2 that are provided with in upright arrangement; Fig. 7 b is four cylinder holes 2 that a circumference 50 and 34 4 crosspoint places of quarterline are provided with; Fig. 7 c has two circumferences 50,51 and 67 4 crosspoint places of bisector four cylinder holes 2 that are provided with in upright arrangement; Fig. 7 d is six cylinder holes 2 with two circumferences 50,51 and 25 6 crosspoint places settings of trisection line; Fig. 7 e is eight cylinder holes 2 with two circumferences 50,51 and 34 8 crosspoint places settings of quarterline; Fig. 7 f has ten cylinder holes 2 that 680 crosspoint places of two circumferences 50,51 and five bisectrixs are provided with etc.

Roller shaft of the present invention is the roller shaft that is had a plurality of shaft parts by the middle part to peripheral isogonism setting, the middle part can be provided with through hole 55, because the nearly outer end of each shaft part all is equipped with roller on inner chamber geosynclinal convex race inner circumference cam profile, therefore freely support non-cantilever beam structure for two ends at least.Fig. 5 a is the straight roller shaft 16 that the isogonism setting has two shaft parts; Fig. 5 b is the Samsung roller shaft 16a that the isogonism setting has three shaft parts; Fig. 5 c is the four stars roller shaft 16b that the isogonism setting has four shaft parts; Fig. 5 d is five-pointed star roller shaft 16c with five shaft parts of isogonism setting etc.Cross section with interior shaft part is a rectangle or I-shaped to the above-mentioned rollers axle in installation roller position, to alleviate the roller shaft tortuosity; Its raw material can use metallic steel or light weight, aluminium, Ti metal alloy that intensity is big or have carbon fiber and other nonmetallic material, alleviates the back and forth movement inertial mass.

Above-mentioned and at least two roller shafts that the cylinder hole matches are provided with side opening 17 and have a shape lower piston bar 5a2b and be installed on the roller shaft side opening 17 with bearing pin 54 in the position that piston rod 5a is installed, as Fig. 6 b2, Fig. 8; Or the single pin piston rod 5a with circular arc lower end cooperates installation with the roller shaft with arc groove 80, does not break away from roller shaft 16 with fastener and bearing pin 54 control piston bar 5a, can allow the piston rod upper end slightly swing at the roller shaft axial plane again.Above-mentioned fastener can be that this type fastener of type can also increase by one and promptly uses its bi-side and fixed guide 4a, 4b slide relative as guide runner 27 to function.All piston rod is installed, as Fig. 6 a1 in hinged mode; Certainly do not get rid of yet piston rod is installed in the mode of rigidly fixing.

Roller shaft of the present invention and peripheral cam profile have identical double peak to valley or four peaks, four paddy inner chamber groove cams 6 or 6b matched is straight roller shaft 16; That have that identical three peaks, three paddy inner chamber groove cam 6a match with the peripheral cam profile is Samsung roller shaft 16a; That have that identical four peaks, four paddy inner chamber groove cam 6b match with the peripheral cam profile can be four stars roller shaft 16b; That have that identical five peak five cereals inner chamber groove cams match with the peripheral cam profile is five-pointed star roller shaft 16c etc.

Main roller of the present invention 9 and or auxilliary roller 37 outer surfaces be cylindrical or taper, with above-mentioned inner chamber groove cam have intilted go up peripheral cam profile 7 and or down peripheral cam profile 8 match, as Fig. 9, purpose is to alleviate " knuckle effect ", also is convenient to adjust simultaneously the gap of main and auxiliary roller in inner chamber geosynclinal convex race.Above-mentioned main roller 9 always contacts with following peripheral cam profile 8, does not contact with last peripheral cam profile 7; And auxilliary roller 37 always contacts with last peripheral cam profile 7, does not contact with following peripheral cam profile 8, so main roller 9 and auxilliary roller 37 when piston rod assembly pumps work, can not produce the torque opposite sign.Use densely covered rolling bearing of cylindrical roller or sliding bearing in the main roller 9, to strengthen bearing capacity; Its each relative motion surface all has high hardness, the high abrasion character of carbonitrided case; Auxilliary roller 37 uses ball bearing.

Guide roller of the present invention or slide block 27, employed guide runner 27 have the through hole 55 that can be inserted in roller shaft in the middle of being, this hole is similar to the section gabarit that roller shaft is installed the slide position, as Figure 10 a, 10b.Slide block 27 is fabricated metalss, and (low carbon steel, low-carbon alloy steel, alloy aluminum etc., its slip surface is carburizing or carbonitriding quench-hardened case or ceramic coating) or ceramic products, improve abrasion resistance, increase the service life.

The axial circumference in cylinder body of the present invention 1 lower end is halved and is provided with two to six a kind of to six equally divided positions and all has two-sided fixed guide 4; As Fig. 7 a, Fig. 7 c is that the second-class office of circumference is provided with two fixed guides; Fig. 7 d is that the third-class office of circumference is provided with three fixed guides; Fig. 7 b, 7e are that circumference fourth class office is provided with four fixed guides; Fig. 7 f is that circumference five equally divided positions are provided with five fixed guides, or circumference six equally divided positions are provided with six fixed guides etc.Outward edge at fixed guide is provided with positioning boss 4c, with the axial motion of restriction roller shaft; Said fixing slideway 4a, 4b can be can be by the fabricated metals of fixed guide seat 4d dismounting and change, (carbon steel, alloyed steel etc., its slip surface is carburizing or carbonitriding quench-hardened case or ceramic coating) or nonmetal as ceramic products, to improve abrasion resistance, increase the service life.

Above-mentioned cylinder body 1 with fixed guide 4d that the axial circumference in cylinder hole 2 and lower end is provided with is an overall structure or be made up of bolt the bottom 1b that upper body 1a with cylinder hole 2 and lower end have a fixed guide 4 of axial circumference setting.

Inner chamber groove cam power transmission mechanism of the present invention, if use inner chamber groove cam 6 or 6b with identical double peak to valley or four peaks, four paddy, the cylinder-bore 2 that its top matches has coaxial setting of a cylinder or circumference 50 and 67 two crosspoint places of bisector array that two cylinder holes 2 are set, as Fig. 7 a; Or two circumferences 50,51 and 67 4 crosspoint places of bisector array are provided with four cylinders 2, Fig. 7 c; The piston rod 5a bottom that fixes with piston 5 in described cylinder-bore 2 all is contained on the straight roller shaft 16 that is used; At roller shaft 16 nearly two ends two main rollers 9 and two auxilliary rollers 37 are housed, roll on the peripheral cam profile in inner chamber groove cam 6 or 6b groove, form the non-cantilever beam structure of two supportings, piston does not have lateral forces in cylinder; The position that two fixed guides axially being provided with in roller shaft 16 and cylinder lower end 4 are relative, be provided with two guide rollers or slide block 27, in two fixed guides 4, make the reaction force that promotes inner chamber groove cam 6 or 6b rotation, act on the face of two fixed guides 4 by two guide rollers or slide block 27, it is free state in cylinder wall that piston does not have lateral forces.As Fig. 1, Figure 10, Figure 11, Figure 12, Figure 13.Because cylinder hole 2 is not subjected to the piston lateral force, the useful ceramics surface.

Inner chamber groove cam power transmission mechanism of the present invention, have identical three peaks, three paddy if use, and last peripheral cam profile has the inner chamber groove cam 6a of three breach 12, the cylinder-bore 2 that matches is that the coaxial setting of single cylinder or two peripheral annular lines 50,51 and 25 6 crosspoint places of trisection line are provided with six cylinder holes 2, in single cylinder or six cylinder holes 2 with fixing piston rod 5 bottoms of six pistons, all be contained in fifty-fifty on three the shaft part 16a1 of an asterism roller shaft 16a that are used, as Fig. 6 c, Figure 15; All be equipped with on main roller 9 and the peripheral cam profile of auxilliary roller 37 in inner chamber cam 6a groove in three nearly outer ends of shaft part of roller shaft 16a and roll, form the non-cantilever beam structure of three-point support, piston does not have lateral forces in cylinder wall; The position that axial circumference trisection is provided with in three shaft parts of roller shaft 16a and the cylinder lower end that matches three fixed guides 4 are relative, be provided with three guide rollers or slide block 27 in three fixed guides 4, make and promote the reaction force that inner chamber groove cam 6a rotates, by three guide rollers or slide block 27, act on the face of three fixed guides 4, piston does not have lateral forces in cylinder wall.

Inner chamber groove cam power transmission mechanism of the present invention, if use identical four peaks, four paddy inner chamber groove cam 6b, the cylinder-bore 2 that matches, also can design 34 4 crosspoint places of peripheral annular line 50 and quarterline four cylinder holes 2 are set, as Fig. 7 b, or two peripheral annular lines 50,51 and 34 8 crosspoint places of quarterline are provided with eight cylinder holes 2, as Fig. 7 e; With four cylinders or four fixing or eight piston rod 5 bottoms of 2 inner carriers 5, eight cylinder cylinder holes, all be contained in fifty-fifty on four shaft part 16b1 of a four stars roller shaft 16b who is used; In four nearly outer ends of shaft part of roller shaft 16b, four auxilliary rollers 37 and four main rollers 9 are housed, roll on the peripheral cam profile in inner chamber groove cam 6b groove, form the non-cantilever beam structure of four-point supporting, piston does not have lateral forces in cylinder; The position that the axial circumference quartering is provided with in four shaft parts of roller shaft 16b and the cylinder lower end that matches four fixed guides 4 are relative, be provided with four guide rollers or slide block 27, in four fixed guides 4, make and promote the reaction force that inner chamber groove cam 6b rotates, by four guide rollers or slide block 27, act on the face of four fixed guides 4, therefore, piston does not have lateral forces in cylinder yet, as Figure 14, Figure 16.

Inner chamber groove cam power transmission mechanism of the present invention, also can use five identical peak five cereals, and last peripheral cam profile has the inner chamber groove cam of five breach 12, join two circumferences 50,680 crosspoint places of 51 and five bisectrixs are provided with ten cylinder holes 2, as Fig. 7 f, match with a five-pointed star roller shaft 16c, with ten fixing piston rod 5a bottoms of 2 inner carriers 5, ten cylinder holes, all be contained in fifty-fifty on five shaft parts of a five-pointed star roller shaft that is used, in five nearly outer ends of shaft part of roller shaft 16c, five auxilliary rollers 37 and five main rollers 9 are housed, roll on the peripheral cam profile in five peak five cereals inner chamber geosynclinal convex races, form the non-cantilever beam structure of 5 supportings, piston does not have lateral forces in cylinder; The position that axial circumference five five equilibriums are provided with in five shaft parts of roller shaft 16c and the cylinder lower end that matches five fixed guides 4 are relative, be provided with five guide rollers or slide block 27, in five fixed guides 4, make and promote the reaction force that inner chamber groove cam 6b rotates, by five guide rollers or slide block 27, act on the face of five fixed guides 4, therefore, piston does not have lateral forces in cylinder yet.

Inner chamber groove cam power transmission mechanism of the present invention, between inner chamber groove cam lower end and the end face bearing, be made as sliding bearing between slide block and the fixed guide, all be the plane motion lower pair promptly, design area is well-to-do, and working pressure lubricant oil forms lubricating pad supporting inner chamber groove cam and slide block.Its part lubricating system and oil duct are, drive the through hole 6i of oil pump 42 pressure oil output by inner chamber groove cam lower end output shaft to inner chamber groove cam lower end surface and upper end, the oil duct that upwards communicates through upper-end surface bearing 33a circular groove 33a1 and through hole thereof with the hole 66 that has on 4 of the fixed guides, as Fig. 3, again by slide block 27 these holes 66 of sealing.If main roller 9, auxilliary roller 37 use rolling bearing, then fixed guide seat 4d side also is provided with little spray orifice 78 and communicates with oil duct, is used for roller shaft and rises to four fens to about three, the lubricant oil directive main roller 9 of spray orifice 78 ejections, it is lubricated, cools off, as Figure 10 a; If main roller 9 uses sliding bearing, then the slip surface of slide block 27 just is provided with the hole of leading to roller shaft core duct, has the hole that communicates with roller shaft axle core duct in the position of roller shaft installation main roller 9 and is used to lubricate, cools off main roller 9, as Figure 10 b.

When the main roller 9 of nearly each outer end of above-mentioned rollers axle and auxilliary roller 37 roller shaft of packing into, the main and auxiliary roller in available snap ring 18 location; When the main and auxiliary roller of nearly each outer end of roller shaft is optionally installed sealing piece 13 by the breach 12 of the last peripheral cam profile 7 inner chamber geosynclinal convex race of packing into, with screw 23 fixing sealing pieces 13 sealing breach 12.

Inner chamber groove cam power transmission mechanism of the present invention, if use double peak to valley inner chamber groove cam to circle for 6 times, to-and-fro motion assembly (piston rod 5, main roller 9, auxilliary roller 37, the axis of rolling 16, guide roller or slide block 27) pumps four times; Circle if use three peaks, three paddy inner chamber groove cam 6a to return, to-and-fro motion assemblies such as piston rod pump six times; Circle if use four peaks, four paddy inner chamber groove cam 6d to return, to-and-fro motion assemblies such as piston rod pump eight times; Therefore, peak, paddy increase a pair of, circle when the inner chamber groove cam returns, and to-and-fro motion assemblies such as piston rod pump to be increased by twice.

Conspicuous effect has: 1, the present invention does not install piston, and the roller of described roller shaft and each outer end just can normally carry out straight line motion and the conversion that rotatablely moves with the inner chamber groove cam, and is simple in structure.2, can be easy to design the piston motion curve of the required the best of various motors, when the peripheral cam profilogram is designed to work done for revising curve of equal velocity, it is constant that the load of piston head changes the branch line of force and the inner chamber groove cam axis of rotation linear distance that promote the rotation of inner chamber groove cam into, during piston head working medium isobaric expansion, just can realize waiting moment of torsion output.3, in internal-combustion engine, can obtain the very big acceleration of piston expansion space stroke, the timely expansion working of high-temperature combustion gas, the maximum explosive force of piston head changes the moment peak torque into, reduces the heat transfer loss of combustion gas to cylinder wall, improve the thermal efficiency, reduced delivery temperature again.4, in Stirling engine, when design of cam profile curve is become to have to go up the stop curve, just obtain the piston discontinuous fluid.5, the peripheral cam profile design is become identical, double peak to valley at least, the inner chamber groove cam rotates a circle, and piston has four strokes at least, and when rotating speed was identical with the connecting rod engine speed, power per liter, power-weight ratio doubled at least.The reaction component of force vertically acts on two fixed guide faces by guide roller on the roller shaft or slide block 27 at least when 6, rotating owing to cam profile; And each outer end of roller shaft all is equipped with roller and is had two fulcrums at least, forms non-overhang, and piston is a free state, does not have active force to put on the cylinder wall, and cylinder is not born supporting functions; Again because of piston does not swing in cylinder, piston and casing wall, piston ring groove does not produce relative fricting movement with the piston ring end face, has improved cylinder, piston and piston ring working life.7, since roller shaft away from the piston head of high temperature, the piston skirt circumferential thickness is even, piston needn't be made ellipse, piston is programmable very short, enough guiding, ring installation just can, make, processing is simple.8, in big load power transmission mechanism, the piston head total load is born simultaneously by two rollers at least, alleviates the load that every roller bears, again because of having increased auxilliary roller 27, main roller 9 can not produce torque to number and reduce heavy wear factor, the working life of improving roller.9, between inner chamber groove cam lower end surface and the end face bearing and all be the plane motion lower pair between slide block and the fixed guide face, working pressure is lubricated just can to obtain the perfect fluid friction, the mechanical efficiency height.10, internal combustion engine use inner chamber groove cam power transmission mechanism, can directly use existing ripe, cylinder cap with distribution devices such as valve, distribution cam axles, and use circular cylinder, the piston that is easy to process and have ripe, intimate perfect piston ring packing technology, inheritance is good, reduces redesign, manufacturing, cost of developing.11, the inner chamber groove cam has the attribute of flywheel, need not increase flywheel in addition, motor in light weight.12, inner chamber groove cam circumference lifting curve is all identical, to fall the journey curve also identical, and dynamic and static balance is good, does not have the oscillating motion body, shakes for a short time, and running steadily.13, close by simple (2 cylinders, 4 cylinders, 6 cylinders, 8 cylinders, 10 cylinders, 12 cylinders) cylinder array, obtain the serial internal-combustion engine of various different capacities easily.14, needn't the complete machine disintegration take out piston rod or roller shaft, just replaceable piston ring or main and auxiliary roller are convenient to repair the maintenance efficiency height.15, the each half cylinder of multicylinder engine work done, cylinder utilization ratio height.16, the present invention can be used as inside and outside combustion machine, and the movement conversion power transmission mechanism of gas, hydraulic motor or pump is used wide.

Description of drawings

Basic structure and embodiment's description of drawings:

The roller shaft of the reciprocal parallel motion of Fig. 1 and the inner chamber groove cam transfer mechanism master sectional view that rotatablely moves.

Fig. 1 a single cylinder inner chamber groove cam power delivery machine master sectional view.

Fig. 2 a has four peaks, four paddy inner chamber groove cam 6b sectional views by end cam 46 and 3 combinations of inward flange cam.

Fig. 2 b has three peaks, three paddy inner chamber groove cam 6a sectional views by end cam 46 and 3 combinations of inward flange cam.

Fig. 2 c has master, the plan view of double peak to valley inner chamber groove cam 6.

Fig. 3 pressure lubrication oil circuit partial sectional view.

Fig. 4 a roller shaft 16 nearly two ends main rollers 9 launch to be unkitted sealing piece 13 and have location diagram in identical double peak to valley inner chamber groove cam 6 grooves at circumference.Three main rollers 9 on three shaft parts of Fig. 4 b asterism roller shaft 16a launch to have location diagram in the identical three peaks three paddy inner chamber groove cam 6a grooves at the circumference that sealing piece 13 is housed.Four main rollers 9 on four shaft parts of Fig. 4 c four stars shape roller shaft 16b expand into location diagram in identical four peaks, the four paddy inner chamber groove cam 6b grooves at the circumference that sealing piece 13 is housed.

Fig. 5 a can adorn a shape lower piston 5a2b, has straight roller shaft 16 main, the plan views that two side openings 17 are arranged on center hole 55 and two shaft parts.Fig. 5 b have center hole 55 and outwards isogonism be provided with six asterism roller shaft 16a master, the plan views that the side opening 17 of six piston rod 5a2b door shape bottoms is installed only arranged on three shaft parts.Fig. 5 c have center hole 55 and outwards isogonism be provided with eight four stars shape roller shaft 16b master, the plan views that the side opening 17 of eight piston rod 5a2b door shape bottoms is installed only arranged on four shaft parts.Fig. 5 d have center hole 55 and outwards isogonism the five-pointed star shape roller shaft 16d plan view of five shaft parts is set.

The bolt 23 that Fig. 6 has a loop wire 79 is fixed on partial sectional view on the piston rod 5a to piston 5.Single pin piston rod 5a1 bottom of Fig. 6 a and roller shaft are installed sketch.Fig. 6 b1 both feet humanoid bottom of piston rod 5a2a and roller shaft 16 are installed sketch.Fig. 6 b2 both feet piston rod 5a2b door shape bottom and roller shaft are installed sketch.Sketch is installed with the Samsung roller shaft 16a that matches in Fig. 6 c tripod piston 5a3 bottom.Sketch is installed with the four stars roller shaft 16b that matches in Fig. 6 d four pin piston rod 5a4 bottoms.The main plan view of Fig. 6 e bolt 23.

Two of 67 liang of crosspoint places of Fig. 7 a circumference 50 and bisector, two cylinder-bore 2 that are provided with in upright arrangement and the straight roller shaft 16 that matches and the second-class offices of circumference be the position diagrammatic top view of guide shaft 4 fixedly.Four cylinder-bore 2 that 34 4 of Fig. 7 b circumference 50 and quarterlines are provided with the intersection point place and the position diagrammatic top view of four fixed guides 4 of four stars roller shaft 16b that matches and circumference fourth class office.Four cylinder-bore 2 that 67 4 crosspoint places of double circumference 50,51 of Fig. 7 c and bisector are provided with and the position diagrammatic top view of two fixed guides 4 of straight roller shaft 16 that matches and the second-class office of circumference.Six cylinder-bore 2 that 25 6 crosspoint places of double circumference 50,51 of Fig. 7 d and trisection line are provided with and the position diagrammatic top view of three fixed guides 4 of Samsung roller shaft 16a that matches and the third-class office of circumference.Eight cylinder-bore 2 that 34 8 crosspoint places of double circumference 50,51 of Fig. 7 e and quarterline are provided with and the position diagrammatic top view of four fixed guides of four stars roller shaft 16b that matches and circumference fourth class office.Ten cylinder-bore 2 that 680 crosspoint places of double circumference 50,51 of Fig. 7 e and five bisectrixs are provided with and the position diagrammatic top view of the five-pointed star roller shaft 16c that matches and five fixed guides 4 of circumference five equally divided positions.

Fig. 8 has a shape lower piston bar 5a2b and the roller shaft installation diagram with side opening 17.Fig. 8 a1 is that single pin piston rod 5a1 and slide block 27 (or fastener 81) with circular arc lower end all are installed in the plan view that roller shaft 16 has arc groove 80 positions.Fig. 8 a2 is the left sectional view of Fig. 8 a1.Fig. 8 b1 has the plan view that circular arc lower end single pin piston rod 5a1 and the roller shaft 16 with arc groove 80 are installed in hinged way; Fig. 8 b2 is the plan view of Fig. 8 b1.

Fig. 9 has the main roller 9a of taper, auxilliary roller 27a, the inner chamber groove cam have intilted on partial sectional view on peripheral cam profile 7 and the following peripheral cam profile 8 groove inner circumference cam profiles.

Figure 10 a has the partial sectional view of the little spray orifice 78 of aiming at main roller 9 use rolling bearings on fixed guide seat 4d.When Figure 10 b uses the main roller 9 of sliding bearing, on the hole 66 of fixed guide face 4a, 4b on the fixed guide seat 4d and slide block 27, lead to the oil duct partial sectional view that main roller 9 is arrived in 16 core holes of roller shaft again.

The single-cylinder four-stroke internal-combustion engine master sectional view that Figure 11 is made of inner chamber groove cam 6.

The twin-tub quartastroke engine master sectional view that Figure 12 a is made of inner chamber groove cam 6.The twin-tub quartastroke engine master sectional view that Figure 12 b 1 is made of inner chamber groove cam 6.The twin-tub quartastroke engine plan view that Figure 12 b2 is made of inner chamber groove cam 6.

The in-line four cylinder quartastroke engine master sectional view that Figure 13 a is made of double peak to valley inner chamber groove cam 6.The in-line four cylinder quartastroke engine diagrammatic top view that Figure 13 b is made of double peak to valley inner chamber groove cam 6.

The circumference four cylinder four-stroke internal-combustion engine master sectional view that Figure 14 a is made of double peak to valley inner chamber groove cam 6.The circumference four cylinder four-stroke internal-combustion engine diagrammatic top view that Figure 14 b is made of double peak to valley inner chamber groove cam 6.

The double six cylinder four-stroke internal-combustion engine sectional views of circumference that Figure 15 a is made of three peaks, three paddy inner chamber groove cam 6a.The double six cylinder four-stroke internal-combustion engine diagrammatic top view of circumference that Figure 15 b is made of three peaks, three paddy inner chamber groove cam 6a.

The double eight cylinder four-stroke internal-combustion engine sectional views of circumference that Figure 16 a is made of four peaks, four paddy inner chamber groove cam 6b.The double eight cylinder four-stroke internal-combustion engine diagrammatic top view of circumference that Figure 16 b is made of four peaks, four paddy inner chamber groove cam 6b.

The unidirectional valve seat 77 of Figure 17 partial sectional view on cylinder body 1.Figure 17 a is installed on the local main sectional view that pneumatic reciprocal suction booster communicates with cam box on the cylinder body 1.Figure 17 b is installed on the main sectional view that reciprocal suction booster does not communicate with cam box on the cylinder body 1.

The Stirling engine master sectional view that Figure 18 a is made of two cover single cylinder inner chamber groove cam power transmission mechanisms.Two main rollers 9 of inner chamber groove cam power transmission mechanism of Figure 18 b Stirling engine ram and two main rollers 9 of distribution cylinder inner chamber groove cam power transmission mechanism, the position circumference launches the phase place sketch on the peripheral cam exterior feature 8 under inner chamber groove cam separately.

Gas, hydraulic motor master sectional view that Figure 19 a is made of two cover single cylinder inner chamber groove cam power transmission mechanisms.Figure 19 b gas, hydraulic motor is with two cover single cylinder inner chamber groove cam power transmission mechanisms, two main rollers 9 at roller shaft 16 near two ends separately, the position circumference expansion phase place sketch under inner chamber groove cam separately on the peripheral cam exterior feature 8.

The pump master sectional view that Figure 20 single cylinder inner chamber groove cam power transmission mechanism constitutes.

The single cylinder two-stroke internal-combustion engine master sectional view that Figure 21 is made of inner chamber groove cam 6.

As follows referring to each title of accompanying drawing:

1 cylinder body (lid), 2 cylinder holes (pilot hole), 3 inward flange cams, 4 fixed guides, 4a, 4b is mounted in the fixed guide face on the fixed guide seat, 4c fixed guide positioning boss, 4d fixed guide seat, 5 pistons, 5a piston rod, the single pin piston rod of 5a1, the humanoid piston rod of 5a2a both feet, 5a2b both feet door shape piston rod, 5a3 tripod piston rod, 5a4 four pin piston rods, 6 double peak to valley inner chamber groove cams, 6a three peaks three paddy inner chamber groove cams, 6b four peaks four paddy inner chamber groove cams, 6i inner chamber groove cam upper and lower end face through hole, peripheral cam profile on the 7 inner chamber groove cams, peripheral cam profile under the 8 inner chamber groove cams, 9 main rollers, 9a taper main roller, 10 output shafts, 11 valves, 12 breach, 13 breach sealing piece, 14 inner chamber groove cams upper end center hole, 15 cam supporting masses (cam box), 16 straight roller shafts, 16a asterism roller shaft, three shaft parts of 16a1 asterism roller shaft, 16b four stars shape roller shaft, four shaft parts of 16b1 roller shaft, 16c five-pointed star shape roller shaft, 17 roller shaft side openings, 18 jump rings, 19 gas ports, 20 partial cutaway sight lines, 21 bearings, 22 inner chamber geosynclinal convex race inner via holes, 23 fixing bolts, 24 oil sealings, 25 trisection lines, 26 scavenging ports, 27 guide rollers or slide block, 28 cylinder caps, the peak of 29 peripheral cam profiles, 30 is the paddy of peripheral cam profile, 31 works done (air inlet) profilogram, 32 exhausts (compression) profilogram, 33a upper-end surface bearing, 33a1 upper-end surface bearing annular oil grove, 33b lower end surface bearing, 34 quarterlines, 35 distribution cam axles, 36 timing gears, 37 auxilliary rollers, roller is assisted in the 37a taper, 38 driving gears, 39 retainingf keys, 40 umbrella teeth, 41 o'clock rule chains or time rule belt, 42 oil pump, 43 timing gears, 44 leaf valves, 45 cam box side openings, 46 end cams, 47 distribution transmission axle head umbrella shape teeth, 48 distribution transmission shafts, 49 distribution transmission shaft timing gear, 50 cylindrical contours, 51 inner circumference lines, 52 synchronous dotted lines, 53 install the screw of sealing piece 13,54 bearing pins, 55 through holes, 56 heaters, 57 regenerators, 58 coolers, 59 transmission shafts, 60 selector valves, the 60a valve seat that commutates, the 60b changeover valve core, 61 tumbler gears, 62 suction ports, 63 relief openings, 64 air flues, 65 oil ducts, 66 oilholes, 67 bisectors, 68 5 bisectrixs, 69 breather check valves, 70 outgassing nonreturn valves, 71 free-pistons, 73 pneumatic reciprocating pumps, 74 guide rods, the 75 air inlet mouths of pipe, 76 mouths of pipe of giving vent to anger, 77 unidirectional valve seats, 78 little spray orifices, 79 loop wires, 80 arc grooves, 81 fasteners.

Embodiment

Embodiment one: single cylinder two-stroke internal-combustion engine such as Figure 21 that inner chamber groove cam power transmission mechanism constitutes.Comprise an inner chamber groove cam 6, cylinder head 28, be provided with the cylinder body 1 of a cylinder hole 2 and relief opening 63, scavenging port 26, piston 5 and piston rod 5a2a, 9, two auxilliary rollers 37 of two main rollers, two guide rollers or slide block 27,16, two fixed guides 4 of a roller shaft, suction port 62, cam box 15.Inner chamber groove cam 6 is housed in cam box 15, and its top is being provided with the cylinder body 1 that cylinder head 28 is housed and has the cylinder hole 2 of setting coaxial with it and is being fastened on the cam box 15; A roller shaft 16 is housed to the piston rod 5a2a lower vertical that fixes with piston 5 in cylinder hole 2, in roller shaft 16 nearly two ends and the right positions of peripheral cam profile phase, two main rollers 9 are housed, two auxilliary rollers 37 are packed into by two breach 12 of peripheral cam profile on the inner chamber groove cam 6 and to be rolled on the inherent peripheral cam profile of groove; The axial circumference relative position of two fixed guides being provided with 4 of halving is provided with two guide rollers or slide block 27 in roller shaft 16 and cylinder lower end, in two fixed guides 4, but scroll-up/down or slip.Be provided with suction port 62 and Reed Valve 44 in cam box 15 sides, the scavenging port 26 that has relief opening 63 to communicate with cam box 15 in addition on cylinder-bore 2 walls.

Embodiment two: with single-cylinder four-stroke internal-combustion engine such as Figure 11 of inner chamber groove cam power transmission mechanism formation, comprise: inner chamber groove cam 6, the cylinder head 28 of part distribution devices such as valve and distribution cam axle is housed, has 1, one piston 5 of cylinder body and the piston rod 5a2a in a cylinder hole 2, two main rollers 9,37, two guide rollers of two auxilliary rollers or 27, one roller shafts 16 of slide block, article two, fixed guide 4, cam box 15.Inner chamber groove cam 6 is housed in cam box 15, and its top is provided with the cylinder body 1 that above-mentioned cylinder cap 28 is housed and is fastened on the cam box 15; The piston rod 5a2a lower vertical that fixes with piston 5 in the cylinder-bore 2 on cylinder block 1 is equipped with a roller shaft 16, in roller shaft 16 nearly two ends and the right position of inner chamber groove cam peripheral cam profile phase, auxilliary roller 37 and main roller 9 all are housed, by two breach 12 of peripheral cam profile 7 correspondences on the inner chamber groove cam 6, roll on the inherent peripheral cam profile of inner chamber groove cam 6 grooves of packing into; The axial circumference relative position of two fixed guides being provided with 4 of halving is provided with two guide rollers or slide block 27 in roller shaft 16 and cylinder lower end, but scroll-up/down or slip in two fixed guides 4.

Distribution cam axle 35 on cylinder head 28, it is umbrella tooth 40 by inner chamber groove cam 6 lower ends, umbrella tooth 47 engagements of distribution transmission shaft 48 1 ends that are provided with cam box 15 lower, transverse, by between the timing gear 36 of the timing gear 49 of distribution transmission shaft 48 outer ends and distribution cam axle 35 ends, time spent rule belt or the time rule chain 41 connect and carry out transmission.

Single-cylinder double stroke, quartastroke engine that above-mentioned inner chamber groove cam power transmission mechanism constitutes, the inner chamber groove cam 6a that can use the peripheral cam profile to launch to have identical three peaks three paddy joins a tripod piston rod 5a3 and asterism roller shaft 16a such as Fig. 6 c, add three main rollers 9, three auxilliary rollers 37, three guide rollers or slide block 27, article three, fixed guide 4, and cam box 15 is formed.When using inner chamber groove cam 6, it whenever circles, and four-stroke internal combustion engine distribution camshaft 35 also rotates a circle, the piston work done once, twice of two stroke IC engine piston work done.When using inner chamber groove cam 6a, in its two weeks of revolution, four-stroke internal combustion engine distribution camshaft 35 rotates three circles, piston work done three times; Two stroke IC engine piston work done six times.When using inner chamber groove cam 6b whenever to circle, alkene machine distribution cam axle 35 rotates two weeks, twice of piston work done in the four-stroke; Two stroke IC engine piston rod work done four times.Conventional single cylinder connecting rod quartastroke engine, bent axle rotated for two weeks, and a work done is once; Obviously, single-cylinder double stroke of the present invention, quartastroke engine cylinder utilization ratio, power per liter, power-weight ratio improve twice at least.

Embodiment three: array two cylinder four-stroke internal-combustion engines such as Figure 12 a12b that inner chamber groove cam power transmission mechanism constitutes.Comprise inner chamber groove cam 6 or 6b, the cylinder cap 28 of part distribution devices such as valve and distribution cam axle 35 is housed, 5, two piston rod 5a of 1, two piston of cylinder body with two cylinder holes 2, two main rollers 9,37, two guide rollers of two auxilliary rollers or 27, one roller shafts 16 of slide block, article two, fixed guide 4, cam box 15.Inner chamber groove cam 6 is housed in cam box 15, and its top is being provided with the cylinder body 1 that cylinder cap 28 is housed and is being fastened on the cam box 15; Two piston rod 5a bottoms that fix with two pistons 5 in two cylinder-bore 2 on cylinder body 1 all are contained on the roller shaft 16 of a perpendicular setting, force two pistons 5 and roller shaft 16 to form the integral body that pumps simultaneously; In roller shaft 16 nearly two outer ends and the right position of inner chamber groove cam peripheral cam profile phase, two auxilliary rollers 37 and two main rollers 9 are housed, pack into by two breach 12 of last peripheral cam profile and roll on the inherent peripheral cam profile of groove; The axial circumference relative position of two fixed guides that are provided with in upright arrangement 4 of halving is provided with two guide rollers or slide block 27, in two fixed guides 4 in roller shaft 16 and cylinder lower end.

The distribution cam axle 35 of distribution device, be umbrella tooth 47 engagements by umbrella tooth 40 with the distribution transmission shaft 48 of cam box 15 lower, transverse setting of inner chamber groove cam 6 lower ends, between the timing gear 36 of the timing gear 49 of distribution transmission shaft 48 outer ends and distribution cam axle 35 ends, time spent rule belt or the time rule chain 41 connect and carry out transmission, as Figure 12 a.A distribution transmission shaft 48 that also can use two distribution cam axles, 35 front end umbrella teeth 40 and inner chamber groove cam 6 or center, 6b upper end on two cylinder caps 28 upwards to be provided with passes the upper end that roller shaft 16 is provided with middle part through hole 55 and has umbrella shape tooth 47 engagement driving such as Figure 12 b1, Figure 12 b2.

The inlet and outlet cam design of above-mentioned two cylinders is become each other the Eight characters up and down, and promptly phase difference is made as 180 degree, and two piston rods 5 are moved upward at every turn a piston rod just being arranged is compression stroke, and the another piston rod is an exhaust stroke simultaneously; When two pistons moved downward at every turn, it was at power stroke that a piston is always arranged, and the another piston is an aspirating stroke simultaneously.Above-mentioned inner chamber groove cam 6 rotates weeks, and distribution cam axle 35 also rotates a circle, two each works done of cylinder once, i.e. twice of work done; If use inner chamber groove cam 6b to rotate a week, 35 two weeks of rotation of distribution cam axle, two each works done twice of cylinder, i.e. work done four times; Conventional two cylinder connecting rod internal-combustion engines, bent axle rotates a week, has only a cylinder work done, i.e. work done once, when rotating speed was identical, obviously, cylinder of internal-combustion engine utilization ratio of the present invention, power per liter, power-weight ratio improved twice and four times respectively.

Embodiment four: with in-line four cylinder quartastroke engine such as Figure 13 of inner chamber groove cam power transmission mechanism formation, comprise: inner chamber groove cam 6 or 6b, part distribution devices such as valve and distribution cam axle 35 and the cylinder cap 28 with four firing chambers are housed, array is provided with the cylinder body 1 in four cylinder holes 2, four pistons 5, four piston rod 5a, 9, two auxilliary rollers 37 of two main rollers, two guide rollers or slide block 27,16, two fixed guides 4 of a roller shaft, cam box 15.An inner chamber groove cam 6 is housed in cam box 15, and its top is provided with cylinder cap 28 to be housed and to have the cylinder body 1 that array is provided with four cylinder holes 2 and is fastened on the cam box 15; Four piston rod 5a bottoms of four cylinder hole 2 interior four pistons 5 all are contained on the roller shaft 16 of perpendicular setting, make four piston rods 5 and roller shaft 16 form the integral body that pumps simultaneously; In roller shaft 16 nearly two ends and the right position of inner chamber groove cam peripheral cam profile phase, two auxilliary rollers 37 and two main rollers 9 are housed, pack into by two breach 12 of peripheral cam profile 7 on the inner chamber groove cam 6 and to roll on the inherent peripheral cam profile of groove, the position that two fixed guides axially being provided with in roller shaft 16 and cylinder body 1 lower end 4 are relative, be provided with two guide rollers or slide block 27, in two fixed guides 4, can slide up and down or roll.

Distribution cam axle 35 on above-mentioned cylinder head 28, it is umbrella tooth 40 by inner chamber groove cam 6 lower ends, umbrella tooth 47 engagements of distribution transmission shaft 48 1 ends that are provided with cam box 15 lower, transverse, between the timing gear 36 of the timing gear 49 of distribution transmission shaft 48 outer ends and distribution cam axle 35 ends, time spent rule belt or the time rule chains 41 carry out transmission, as Figure 11,12a distribution drive part.The distribution transmission shaft 48 that two distribution cam axles, 35 front end umbrella teeth 40 on also available two cylinder caps 28 and inner chamber groove cam 6 or center, 6b upper end upwards are provided with passes the upper end that the roller shaft 16 that matches is provided with middle part through hole 55 and has umbrella shape tooth 47 engagement driving such as Figure 13 a, Figure 13 b.When using inner chamber groove cam 6, it whenever circles, and distribution cam axle 35 also rotates a circle; When using inner chamber groove cam 6b, it whenever circles, 31 two weeks of rotation of distribution cam axle.

Above-mentioned distribution cam axle 35, it is all identical to be designed to the open and close angle to the intake and exhaust cam of two cylinder correspondences outside, makes the air inlet simultaneously of two cylinders, compression, work done, exhaust; It is all identical that intake and exhaust cam in interior two cylinder correspondences is designed to the open and close angle, makes this two cylinder also air inlet simultaneously, compression, work done, exhaust; Allowing outside, the phase difference of the intake and exhaust cam of two cylinders and interior two cylinders is made as 180 degree; Four piston rods are moved downward at every turn, and it is power stroke that two piston rods are all arranged, and two piston rods are aspirating stroke in addition simultaneously; And move upward, it is compression stroke that two piston rods are all arranged, two piston rods are exhaust stroke in addition simultaneously; at every turn Above-mentioned inner chamber groove cam 6 rotates a week, four each works done of cylinder is arranged once, and both work done was four times; If use inner chamber groove cam 6b to rotate a week, four each works done twice of cylinder, i.e. work done eight times, conventional four cylinder connecting rod internal-combustion engines, bent axle rotates a week, has only two cylinder works done; Obviously, cylinder of internal-combustion engine utilization ratio of the present invention, power per liter, power-weight ratio all improve twice and four times.

Embodiment five: four cylinder four-stroke internal-combustion engine such as Figure 14 that the circumference 90 degree isogonisms of being made up of inner chamber groove cam 6b are provided with, comprise: a peripheral cam profile expands into identical four peaks, four paddy, and last peripheral cam profile 7 has the inner chamber groove cam 6b of four breach 12 of isogonism setting, the 90 degree circumference quarterings are provided with four cylinder holes 2 on the cylinder body 1, four all are equipped with valve, the cylinder head 28 of part distribution devices such as distribution cam axle 35, four pistons 5, four piston rod 5a, four main rollers 9, four auxilliary rollers 37, four guide rollers or slide block 27, a four stars roller shaft 16b, axially the circumference quartering is provided with four fixed guides 4, cam box 15; An inner chamber groove cam 6b is housed in cam box 15, and the cylinder body 1 that its top circumference 90 degree quarterings are being provided with four cylinder holes 2 and four cylinder caps 28 are housed is fixed on the cam box 15; In four cylinder holes 2 with four four piston rod 5a bottoms that piston 5 fixes, be installed in respectively on four shaft parts of four stars shape roller shaft 16b of a perpendicular setting, make four pistons 5 and four stars shape roller shaft 16b form the integral body that pumps simultaneously; In four nearly outer ends of shaft part of four stars shape roller shaft 16b and the right position of inner chamber groove cam 6b peripheral cam profile phase, four main rollers 9 and four auxilliary rollers 37 are housed, and four breach 12 going up the peripheral cam profile by inner chamber groove cam 6b are packed into and are rolled on the inherent peripheral cam profile of groove; The position that four fixed guides axially being provided with in four stars shape roller shaft 16b and circumference fourth class office, cylinder lower end 4 are relative is provided with four guide rollers or slide block 27, in four fixed guides 4, but scroll-up/down or slip.

The distribution transmission shaft 48 that four distribution cam axles, 35 front end umbrella teeth 40 on above-mentioned four cylinder caps 28 all upwards are provided with center, inner chamber groove cam 6b upper end passes umbrella shape tooth 47 engagement driving that the upper end of four stars shape roller shaft 16b middle part through hole 55 has; Inner chamber groove cam 6b whenever circles, 35 two weeks of rotation of distribution cam axle.

Distribution cam axle 35 intake and exhaust cams of above-mentioned relative two cylinder head 28 are designed to open, it is all identical to close the angular direction, make 2 air inlets simultaneously of relative two cylinder holes, compression, acting, exhaust; It is also identical that other distribution cam axle 35 intake and exhaust cams of relative two cylinder head 28 are designed to the open and close angular direction, makes 2 air inlets simultaneously of relative two cylinders, compression, work done, exhaust; And relative two cylinders and the inlet and outlet cam phase difference of the distribution cam axle 35 of other relative two cylinders are made as 180 degree; Four piston rods are moved upward at every turn, relative two cylinder compressions, two relative cylinder exhausts are in addition simultaneously always arranged; Move downward at every turn, two relative cylinder works done are always arranged, simultaneously other two relative cylinder intakes.

Above-mentioned four peaks, four paddy inner chamber groove cam 6b circle piston rod to-and-fro motion eight times, four each works done twice of cylinder, i.e. work done eight times; Conventional four cylinder connecting rod internal-combustion engines, bent axle rotates a week, has only two each merits of cylinder once; Obviously, cylinder utilization ratio of the present invention improves four times, and power also improves four times in theory, and power-weight ratio also improves four times.

Embodiment six: six cylinder four-stroke internal-combustion engine such as Figure 15 that inner chamber groove cam power transmission mechanism constitutes, comprise that the peripheral cam profile launches to have identical three peaks, three paddy, last peripheral cam profile has the inner chamber groove cam 6a of three breach 12, three cylinder caps 28 that part distribution device such as air gate distribution camshaft are housed and have two firing chambers, on the double circumference 120 degree trisection lines six cylinder-bore are being set on the cylinder body 1, cylinder-bore 2a as Fig. 7 d setting, 2b, 2c, 2d, 2e, 2f, 2a wherein, 2b, 2c is on same excircle trisection line 25,2d, 2e, 2f is on the trisection line 25 of same inner circumference, six pistons 5, six piston rod 5a, three main rollers 9, three auxilliary rollers 37, three guide rollers or slide block 27, an asterism roller shaft 16a, three fixed guides 4 that the third-class office of circumference axially is provided with, cam box 15.An inner chamber groove cam 6a is housed in cam box 15, its top be provided with six cylinder holes 2 at double circumference 50,51 and trisection line 25 intersection point places and be equipped with three cylinder caps 28, cylinder body 1 be fixed on the cam box 15; With six six piston rod 5a bottoms that piston 5 fixes, on average be installed on three shaft parts of delta/Y shape roller shaft 16a of a perpendicular setting in six cylinder holes 2, form the integral body that six pistons 5 and asterism roller shaft 16a pump simultaneously; In three nearly outer ends of shaft part of asterism roller shaft 16a and the right position of inner chamber groove cam 6a peripheral cam profile phase, three main rollers 9 and three auxilliary rollers 37 are housed, and three breach 12 going up the peripheral cam profile by inner chamber groove cam 6a are packed into and are rolled on the inherent peripheral cam profile of groove; The position that axial circumference trisection is provided with in asterism roller shaft 16a and cylinder lower end three fixed guides 4 are relative is provided with three guide rollers or slide block 27, in three fixed guides 4, but scroll-up/down or slip.

The distribution transmission shaft 48 that the umbrella tooth 40 that three distribution cam axle 35 1 ends on above-mentioned three cylinder caps 28 are installed is all upwards installed with inner chamber groove cam upper end center hole 14 passes the transmission of intermeshing of umbrella shape tooth 47 that the upper end of roller shaft middle part through hole 55 has; Make inner chamber cam 6a two weeks of revolution, every distribution cam axle 35 rotates three circles.

It is all identical that distribution cam axle 35 intake and exhaust cams that the corresponding cylinder of three cylinder-bore 2a, 2b shown in Fig. 7 d, 2c on the above-mentioned cylindrical contour 50 is matched are designed to the open and close angular direction, makes the air inlets simultaneously of three cylinders, compression, acting, exhaust; It is all identical that the intake and exhaust cam that the corresponding cylinder of three cylinder-bore 2d, 2e shown in Fig. 7 d, 2f on the inner circumference line 51 is matched also is designed to the open and close angular direction, makes the air inlets simultaneously of three cylinders, compression, work done, exhaust; And the phase difference of distribution cam axle 35 intake and exhaust cams of three cylinders of cylinder-bore 2a, 2b, 2c correspondence and cylinder-bore 2d, 2e, three cylinders that 2f is corresponding is made as 180 degree; Six piston rod assemblies are moved upward at every turn, and it is compression stroke that three cylinders on the same circumference are always arranged, and other three cylinders are exhaust stroke simultaneously; When six piston rods move downward at every turn, it is power stroke that three cylinders on the same circumference are always arranged, and other three cylinders are aspirating stroke simultaneously.Therefore, above-mentioned inner chamber groove cam 6a rotated for two weeks, and every cylinder work done of six cylinders three times just has 18 works done, and six cylinder connecting rod internal-combustion engines, two weeks of crankshaft rotating, six each works done of cylinder once, i.e. six works done; Obviously, cylinder utilization ratio, power, the power-weight ratio of the present invention's six cylinder four-stroke internal-combustion engines all improve three times.

Embodiment seven: inner chamber groove cam 6b power transmission mechanism constitutes eight cylinder four-stroke internal-combustion engine such as Figure 16, comprise that the peripheral cam profile has identical four peaks, four paddy, and last peripheral cam profile has the inner chamber groove cam 6b of four breach, four cylinder head 28 that part distribution devices such as air gate distribution camshaft are housed, have eight cylinder holes 2 and cylinder body 1, wherein cylinder-bore 2a, the 2b that is provided with as Fig. 7 e, 2c, 2d are on same cylindrical contour 50; Cylinder-bore 2e shown in Fig. 7 e, 2f, 2g, 2h on same inner circumference line 51 as Fig. 7 b, eight pistons 5, eight piston rod 5a, four rollers 9,37, four guide rollers of four auxilliary rollers or 27, one four stars roller shafts of slide block 16b, four fixed guides 4 that circumference fourth class office axially is provided with, cam box 15.An inner chamber groove cam 6b is housed in the cam box 15, the cylinder body 1 that its top is being provided with eight cylinder holes 2 in double circumference 50,51 and quarterline 34 intersections and four cylinder caps 28 are housed is fastened on the cam box 15, in eight cylinder holes 2 and eight eight piston rod 5a bottoms that piston 5 fixes, on average be contained on four shaft part 16b1 of four stars type roller shaft 16b of a perpendicular setting, form the integral body that eight pistons 5 and four stars shape roller shaft 16b pump simultaneously; In each nearly outer end of shaft part 16b1 of four stars roller shaft, with the right position of inner chamber groove cam 6b peripheral cam profile phase, four main rollers 9 and four auxilliary rollers 37 are housed, and four breach 12 going up the peripheral cam profile by inner chamber groove cam 6b are packed into and are rolled on the inherent peripheral cam profile of groove of inner chamber groove cam 6b; At four shaft part 16b1 of four stars shape roller shaft, the position that four fixed guides axially being provided with the cylinder lower end circumference quartering respectively 4 are relative is provided with four guide rollers or slide block 27 in four fixed guides 4.

The upper end that the distribution transmission shaft 48 that the umbrella tooth 40 of four distribution cam axle 35 1 ends on above-mentioned four cylinder caps 28 all upwards is provided with center, inner chamber groove cam 6b upper end passes four stars shape roller shaft 16b middle part through hole 55 has umbrella shape tooth 47 engagement driving; Inner chamber cam 6b whenever circles, every 35 two weeks of rotation of distribution cam axle.It is all identical that distribution cam axle 35 intake and exhaust cams that four cylinder-bore 2a, 2b shown in Fig. 7 e on the cylindrical contour 50, the corresponding cylinder of 2c, 2d are matched are designed to the open and close angular direction, makes the air inlets simultaneously of four cylinders, compression, acting, exhaust; It is all identical that the intake and exhaust cam that four cylinder-bore 2e, 2f shown in Fig. 7 e on the inner circumference line 51, the corresponding cylinder of 2g, 2h are matched is designed to the open and close angular direction, makes these four cylinders air inlets simultaneously, compression, work done, exhaust; And being made as 180, the phase difference of the intake and exhaust cam of the intake and exhaust cam of four cylinders of cylinder-bore 2a, 2b shown in Fig. 7 e, 2c, 2d correspondence and cylinder-bore 2e, 2f, four cylinders that 2g, 2h are corresponding spends; Eight piston rods are moved upward at every turn, always have four cylinders 2 on the same circumference to be compression stroke, the cylinder 2 on other four same circumference is an exhaust stroke simultaneously; Eight piston rods 5 move downward at every turn, always have four cylinders 2 on the same circumference to be power stroke, and the cylinder 2 on other four same circumference is an aspirating stroke simultaneously.

Also any two relative cylinder-bore 2e, 2g or the 2f on distribution cam axle 35 intake and exhaust cams that can match two relative cylinder-bore 2a, 2c on the above-mentioned cylindrical contour 50 shown in Fig. 7 e or the corresponding cylinder of 2b, 2d and the inner circumference line 51, it is all identical that distribution cam axle 35 intake and exhaust cams that the corresponding cylinder of 2h matches are designed to the open and close angle, make any two relative cylinder-bore 2e, 2g or 2f on two cylinder-bore 2a, 2c on the cylindrical contour 50 or the corresponding cylinder of 2b, 2d and the inner circumference line 51, the corresponding cylinder of 2h, air inlet simultaneously, compression, work done, exhaust; Make the working state of other four cylinders identical, both air inlet simultaneously, compression, work done, exhaust; And the phase difference of the inlet and outlet cam of the intake and exhaust cam of four the working state same cylinder in back and preceding four working state same cylinder is made as 180 degree; Therefore when also obtaining each eight piston rod assemblies and moving upward, always have four cylinders 2 to be compression stroke, other four cylinders 2 are exhaust stroke simultaneously; When eight piston rod 5 assemblies move downward at every turn, four cylinder works done are always arranged, simultaneously other four cylinder intakes.

Above-mentioned four peaks, four paddy inner chamber groove cam 6b rotate a circle, piston rod to-and-fro motion eight times, and every cylinder work done twice, totally ten six works done, and eight cylinder connecting rod internal-combustion engines in one week of crankshaft rotating, have four each works done of cylinder once, totally four times; Obviously, cylinder utilization ratio, power, the power-weight ratio of the present invention's eight cylinder four-stroke internal-combustion engines all improve four times.

The foregoing description three is designed to the phase angle of embodiment seven distribution cam axle, and the valve opening of the cylinder correspondence of cylinder sum 1/2nd is closed the corresponding valve opening of all identical inlet and outlet cam in angle and other 1/2nd cylinders, and to close all identical inlet and outlet cam phase difference in angle be 180 ° of angles; Therefore when piston rod assembly moved downward, the piston rod in the cylinder of cylinder sum 1/2nd was an expansion space stroke, and 1/2nd piston bars are intake stroke in addition; When piston rod assembly moved upward, cylinder sum 1/2nd piston bars were exhaust stroke, and 1/2nd piston bar is a compression stroke in addition.

The foregoing description two is equipped with suction tude to the suction port of embodiment seven IC engine cylinder head 28, and relief opening is equipped with outlet pipe and silencing apparatus.

Increasing air inflow is one of important way that improves engine power, and exhaust-gas turbocharger is a modern boosting internal combustion engine mode commonly used, but cost is higher.Internal combustion engine bar of the present invention pumps, and the underpart of the piston rod volume is also corresponding to change, and therefore produces pressure change, as long as increase the inlet, outlet one-way valve, just has the function of pump, increases the air inflow that enters cylinder with this.The air inlet mouth of pipe 75 that breather check valve 69 is housed at side opening 45 places of cylinder block 1 or cam box 15 sides and communicates with atmosphere and the mouth of pipe 76 of giving vent to anger that outgassing nonreturn valve 70 is housed and communicates with the cylinder head suction port are as Figure 17; When piston rod 5 moves upward, the underpart of the piston rod sealed volume produces vacuum, and air is sucked by suction valve 69, and when piston rod 5 moves downward, the underpart of the piston rod air is compressed by gas outlet valve 70 and is pressed into cylinder.Also can utilize the interior pressure change of underpart of the piston rod sealed volume to be power source, drive installation is free-piston 71 or diaphragm in side opening 45 place's free piston types of lateral cylinder surface or cam box side or the pneumatic reciprocating pump 73 of diaphragm type, reach the pipeline that leads to cylinder cap 28 suction ports by the 69 suction air of the breather check valve on the unidirectional valve gap 77 by outgassing nonreturn valve 70 and be pressed into cylinder, as Figure 17 a, Figure 17 b, improve pump gas efficient, cost is low.

The foregoing description one to embodiment seven internal-combustion engine is to be furnished with petrol pump, Carburetor or inlet manifold gas supply system such as electronically controlled gasoline injection device and cylinder head are installed spark plug is installed and is furnished with the gasoline internal combustion engine of ignition systems such as high voltage wire, high-tension coil or is furnished with the diesel internal combustion motor that diesel oil supply systems such as high pressure nozzle are housed on high-pressure injection pump, the cylinder cap.

The foregoing description one to the inner chamber groove cam excircle bottom of embodiment's seven internal-combustion engines is equipped with gear ring and with cam box 15 relative positions starting motor is installed, in order to starting apparatus combustion engine.

The foregoing description one is to embodiment seven internal-combustion engine, and is available air-cooled or water pump, water tank, fan are installed are carried out water-cooled.

Embodiment eight: Stirling engine such as Figure 18 a that inner chamber groove cam power transmission mechanism constitutes comprise two cover single cylinder inner chamber groove cam power transmission mechanisms, heater 56, regenerator 57, cooler 58; Two inner chamber groove cams 6 in two cover single cylinder inner chamber groove cam power transmission mechanisms mesh mutual transmission with parallel way with gear 42; Gas port 19 on cylinder head 28 communicates with heater 56, gas port 19 on the another cylinder head 28 communicates with cooler 58, two main rollers 9 at heater 56 and cooler 58 bottom roller shafts 16 nearly two ends, circumference in wide 8 positions of 6 times peripheral cams of two inner chamber groove cams launches the phase place sketch, as Figure 18 b.Stop peak, two paddy inner chamber groove cam 6 when using two peripheral cam exterior features all to have identical two going up, cooperate bipod lower piston bar 5a2a and roller shaft 16 all to have and stop peak, three paddy inner chamber groove cam 6a on three and join tripod lower piston bar 5a3 and roller shaft 16a such as Fig. 6 c or two and all have and stop peak, four paddy inner chamber groove cam 6b on four, join four piston rod 5a4 of underfooting portion and roller shaft 16b and as Fig. 6 d as Fig. 6 b1 or two; The above inner chamber groove cam power transmission mechanism of also available two covers becomes the multi-cylinder Stirling engine with meshed transmission gear mechanism.

Embodiment nine: gas, hydraulic motor that inner chamber groove cam power transmission mechanism constitutes comprise two cover single cylinder inner chamber groove cam power transmission mechanisms, driving gear 38, tumbler gear 61, selector valve 60, transmission shaft 59; Overlap single cylinder inner chamber groove cam power transmission mechanisms with driving gear 38 is housed separately two, with parallel way and middle tumbler gear 66 engagement driving, middle tumbler gear 61 1 ends are the output shaft of gas motor, the other end be installed in cylinder cap on selector valve 60 between usefulness transmission shaft 59 interlock mutually; Gas port 19 at two cylinder caps 28 all is provided with the air flue 64 that communicates with selector valve 60, as Figure 19 a.Two main rollers 9 at two piston rods, 5 bottom roller shafts, the 16 nearly two ends of two cover single cylinder inner chamber groove cam power transmission mechanisms, the circumference in wide 8 positions of 6 times peripheral cams of two inner chamber groove cams launches the phase place sketch, as Figure 19 b.

Above-mentioned two inner chamber groove cams all have identical double peak to valley or three peaks, three paddy or four peaks, four paddy, the angle of circumference radian of angle of circumference camber ratio exhaust curve 32 projections of work done curve 31 projections of peripheral cam exterior feature is bigger, therefore, as long as suction port enters the working medium of certain pressure intensity, gas, hydraulic motor just wait moment of torsion ground running output power, do not have the dead point.Meshed transmission gear is used in the parallel connection of the above inner chamber groove cam power transmission mechanism of also available two covers, constitutes multi-cylinder gas, hydraulic motor.

Above-mentioned inner chamber groove cam power transmission mechanism constitutes each embodiment: internal-combustion engine, Stirling engine, gas, hydraulic motor, high-power in order to obtain high pulling torque, the curve 31 of descending work done (air inlet) stroke of inner chamber groove cam circumference profile is designed to revise curve of equal velocity, thereby increases the work done acceleration of piston rod assembly; Can be designed to up inner chamber groove cam peripheral cam profile compression (exhaust) curve 32 of piston rod to revise in sinusoidal curve or revise step curve, reduce jerk.

Embodiment ten: straight line motion constitutes gas, liquid pump with the power transmission mechanism of the conversion that rotatablely moves, comprise inner chamber groove cam 6, roller shaft 16, piston 5, piston rod 5a2a, main roller 9, auxilliary roller 37, guide roller or slide block 27, the cylinder head 28 of suction valve 69 and gas outlet valve 70 is installed, be provided with the cylinder body 1 in cylinder hole 2, fixed guide 4, cam box 15.Inner chamber groove cam 6 is housed in cam box 15, the cylinder body 1 that its top is provided with a cylinder hole 2 coaxially and cylinder cap 28 is housed is fastened on the cam box 15, the piston rod 5a2a bottom that fixes with piston 5 in cylinder hole 2 is contained on the roller shaft 16, in the position that roller shaft 16 nearly two outer ends and inner chamber groove cam 6 peripheral cam profile phases are right main roller 9 is housed, auxilliary roller 37 is at inner chamber groove cam 6 peripheral cam profiles; Axially be provided with in roller shaft 16 and cylinder body 1 lower end two fixing relative positions of guide shaft 4 are provided with two guide rollers or slide block 27, in two fixed guides 4, as Figure 20.Order about inner chamber groove cam 6 when external force and rotate, drive piston 5 and pump, the gas or the liquid of piston upper end cavity volume are sucked by suction valve 69, are discharged by gas outlet valve 70.

Above-mentioned inner chamber groove cam power transmission mechanism constitutes each embodiment: internal-combustion engine, Stirling engine, gas, hydraulic motor, in the groove of inner chamber groove cam that main and auxiliary roller is packed into, sealing piece 13 can be installed as required, with the fixing sealing of screw breach 12.Above-mentioned internal-combustion engine with inner chamber groove cam power transmission mechanism and formation, Stirling engine, gas, hydraulic motor, the inboard position relative of its cam box 15 with inner chamber groove cam side opening 22 or breach 12 all have openable sealing cover and with the hole 45 of exterior, be convenient to main roller 9 and auxilliary roller 37 needn't be dismantled cylinder body, need only open this hole 45 dismounting sealing pieces 13, take out snap ring 18 and just can axially draw off easily and the main and auxiliary roller of packing into from the utmost point on the roller shaft.

The motor that the above-mentioned inner chamber groove cam of the present invention power transmission mechanism constitutes can be installed in instrument that various forms can be travelled in the water, land and air (as car, ship, aircraft etc.) or the electric power output device driving force is provided.

Claims (25)

1, a kind of straight line motion and the power transmission mechanism that rotatablely moves and change comprise:
The inner chamber groove cam can be formed with continuous cam path around its axis rotation on its cylindrical cavity wall;
It is characterized in that, also comprise:
Support and hold the cam box (15) of inner chamber groove cam, have the lid (1) that is positioned at the cam box top, and be installed in the fixed guide (4) that extends into the inner chamber of inner chamber groove cam under the lid (1);
Realize the assembly of straight reciprocating motion, comprise that the axis perpendicular to the inner chamber groove cam is provided with roller shaft (16), respectively at the adjacent installation in roller shaft (16) two end part and main roller (9) that in described cam path, moves and auxilliary roller (37), be arranged on that described roller shaft (16) is gone up and along the guiding element (27) of guide rail movement, described roller shaft (16) forms the non-cantilever beam structure that two ends are at least freely supported described in the inner chamber groove cam
Wherein, the motion of described roller shaft (16) is synthetic along the motion of fixed guide (4) simultaneously by main roller (9) and motion and the guiding element (27) of auxilliary roller (37) in cam path.
2, straight line motion according to claim 1 and the power transmission mechanism that rotatablely moves and change is characterized in that described guiding element (27) is roller or slide block.
3, straight line motion according to claim 1 and the power transmission mechanism that rotatablely moves and change, it is characterized in that, described lid (1) is made of piston/cylinder, described cylinder body has piston cylinder hole (2), piston (5) with piston rod (5a) is installed in the piston cylinder hole, one end of described piston rod (5a) links to each other with piston (5), and the other end links to each other with roller shaft (16).
4, straight line motion according to claim 1 and the power transmission mechanism that rotatablely moves and change, it is characterized in that, described inner chamber groove cam has the rotating shaft part, the waveform that is shaped as the identical double peak to valley at least of wave amplitude of its cam path, cam path has overhead cam profile (7) and following cam profile (8), and described main roller (9) and auxilliary roller (37) move between overhead cam profile (7) and following cam profile (8).
5, the power transmission mechanism of straight line motion according to claim 3 and the conversion that rotatablely moves is characterized in that described overhead cam profile (7) has two to five breach (12), is used for roller shaft (16) cam path of packing into.
6, straight line motion according to claim 3 and the power transmission mechanism that rotatablely moves and change, it is characterized in that, described roller shaft (16) comprises by the middle part to be dispersed and n shaft part being provided with of equal angles along the circumferential direction to periphery, described guide rail along the circumferential direction forms corresponding n, and wherein n is the natural number between 2 to 5.
7, straight line motion according to claim 6 and the power transmission mechanism that rotatablely moves and change is characterized in that piston rod (5a) has n pin, and be continuous with corresponding shaft part respectively.
8, straight line motion according to claim 6 and the power transmission mechanism that rotatablely moves and change is characterized in that described piston (5) has n piston rod (5a), and continuous with corresponding shaft part respectively, described cylinder body has n cylinder hole (2).
9, straight line motion according to claim 6 and the power transmission mechanism that rotatablely moves and change, it is characterized in that, n shaft part of corresponding described roller shaft (16) is provided with n cylinder body, each cylinder body has piston (5), piston rod (5a) and cylinder hole (2) respectively, and described piston rod (5a) is continuous with corresponding shaft part respectively.
10, straight line motion according to claim 6 and the power transmission mechanism that rotatablely moves and change, it is characterized in that, corresponding described each shaft part of described cylinder body has m cylinder hole, the cylinder hole adds up to m * n, corresponding each cylinder hole is provided with piston (5), piston rod (5a), described piston rod (5a) is continuous with corresponding shaft part respectively, and wherein m is 1 or 2.
According to the power transmission mechanism of the straight line motion described in the claim 9 with the conversion that rotatablely moves, it is characterized in that 11, described straight line motion constitutes single cylinder two-stroke internal-combustion engine with the power transmission mechanism of the conversion that rotatablely moves, n is 2.
According to the power transmission mechanism of the straight line motion described in the claim 9 with the conversion that rotatablely moves, it is characterized in that 12, described straight line motion constitutes the single-cylinder four-stroke internal-combustion engine with the power transmission mechanism of the conversion that rotatablely moves, n is 2.
13, straight line motion according to claim 10 and the power transmission mechanism that rotatablely moves and change is characterized in that, described straight line motion constitutes two cylinder four-stroke internal-combustion engines in upright arrangement with the power transmission mechanism of the conversion that rotatablely moves, and n is 2, and m is 1.
14, straight line motion according to claim 10 and the power transmission mechanism that rotatablely moves and change is characterized in that, described straight line motion constitutes the in-line four cylinder quartastroke engine with the power transmission mechanism of the conversion that rotatablely moves, and n is 2, and m is 2.
15, according to claim 12,13 or 14 described straight line motions and the power transmission mechanism that rotatablely moves and change, it is characterized in that, described internal-combustion engine is equipped with distribution device, the rotating shaft of inner chamber groove cam (6) is equipped with umbrella gear (40), and it is installed in umbrella gear (47) engagement of distribution transmission shaft (48) one ends, distribution transmission shaft (48) is positioned at cam box (15) bottom perpendicular to the axis of inner chamber groove cam (6), the other end at distribution transmission shaft (48) is equipped with timing gear (49), timing gear (49) and be installed between the timing gear (36) of distribution cam axle (35) one ends time spent rule belt or the time rule chains (41) connect transmission.
16, straight line motion according to claim 9 and the power transmission mechanism that rotatablely moves and change is characterized in that, described straight line motion constitutes the four cylinder four-stroke internal-combustion engine with the power transmission mechanism of the conversion that rotatablely moves, and n is 4.
17, straight line motion according to claim 10 and the power transmission mechanism that rotatablely moves and change is characterized in that, described straight line motion constitutes six cylinder four-stroke internal-combustion engines with the power transmission mechanism of the conversion that rotatablely moves, and n is 3, and m is 2.
18, straight line motion according to claim 10 and the power transmission mechanism that rotatablely moves and change is characterized in that, described straight line motion constitutes eight cylinder four-stroke internal-combustion engines with the power transmission mechanism of the conversion that rotatablely moves, and n is 4, and m is 2.
19, according to claim 12-14, each described straight line motion and the power transmission mechanism that rotatablely moves and change among the 16-18, it is characterized in that, described internal-combustion engine is equipped with and comprises valve, the distribution device of distribution cam axle, described cylinder body has cylinder cap (28), distribution cam axle (35) is installed on the cylinder cap (28), distribution cam axle (35) one ends have umbrella gear (40), distribution transmission shaft (48) passes roller shaft middle part through hole (55) and upwards is provided with along inner chamber groove cam axis, the umbrella shape tooth (47) that has in the upper end of distribution transmission shaft (48), umbrella gear (40) and umbrella gear (47) engagement driving.
20, according to claim 12-14, each described straight line motion and the power transmission mechanism that rotatablely moves and change among the 16-18, it is characterized in that, described internal-combustion engine is equipped with the distribution device that comprises valve, distribution cam axle, and the pairing valve opening of the cylinder body of cylinder body sum 1/2nd is closed the corresponding valve opening of all identical intake cam in angle and other 1/2nd cylinder bodies, and to close all identical intake cam phase difference in angle be 180 degree; The pairing valve opening of the cylinder body of cylinder body sum 1/2nd is closed the corresponding valve opening of all identical exhaust cam in angle and other 1/2nd cylinder bodies, and to close all identical exhaust cam phase difference in angle also be 180 degree.
21, straight line motion according to claim 3 and the power transmission mechanism that rotatablely moves and change, it is characterized in that, the power transmission mechanism of two the described straight line motions and the conversion that rotatablely moves, heater (56), regenerator (57), cooler (58) constitutes two cylinder Stirling engines, described two mechanisms are with gear drive (42) transmission of intermeshing, therein in described mechanism, the gas port (19) of the cylinder cap of cylinder body (28) communicates with heater (56), and in another mechanism, for the gas port (19) of distribution cylinder cylinder cap (28) communicates with cooler (58), and heater (56) and cooler (58) all have a gas port to communicate with regenerator (57).
22, straight line motion according to claim 4 and the power transmission mechanism that rotatablely moves and change is characterized in that, described inner chamber groove cam is that two-part combination that has overhead cam profile (7) and following cam profile (8) respectively fixedly forms.
23, straight line motion according to claim 4 and the power transmission mechanism that rotatablely moves and change, it is characterized in that the downward projection of overhead cam profile (7) working curved surface of described inner chamber groove cam is not overlapping or not exclusively overlapping with following cam profile (8) working curved surface.
24, straight line motion according to claim 4 and the power transmission mechanism that rotatablely moves and change, it is characterized in that, described auxilliary roller (37) contacts engagement with the overhead cam profile (7) of inner chamber groove cam, and main roller (9) contacts engagement with following cam profile (8).
25, straight line motion according to claim 4 and the power transmission mechanism that rotatablely moves and change is characterized in that, overhead cam profile (7) and/or following cam profile (8) are to described cam path inner inclination.
CNB2004100845199A 2004-11-24 2004-11-24 Power transmission mechanism with linear and rotation movement conversion CN100429431C (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CNB2004100845199A CN100429431C (en) 2004-11-24 2004-11-24 Power transmission mechanism with linear and rotation movement conversion

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
CNB2004100845199A CN100429431C (en) 2004-11-24 2004-11-24 Power transmission mechanism with linear and rotation movement conversion
EP20050813805 EP1821001B1 (en) 2004-11-24 2005-11-24 A power transmitting mechanism for the conversion between linear movement and rotary motion
JP2007541651A JP4647664B2 (en) 2004-11-24 2005-11-24 Power transmission mechanism that converts linear motion into rotational motion
US11/791,412 US7584737B2 (en) 2004-11-24 2005-11-24 Power transmission mechanism for conversion between linear movement and rotary motion
PCT/CN2005/001986 WO2006056126A1 (en) 2004-11-24 2005-11-24 A power transmitting mechanism for the conversion between linear movement and rotary motion

Publications (2)

Publication Number Publication Date
CN1779297A CN1779297A (en) 2006-05-31
CN100429431C true CN100429431C (en) 2008-10-29

Family

ID=36497741

Family Applications (1)

Application Number Title Priority Date Filing Date
CNB2004100845199A CN100429431C (en) 2004-11-24 2004-11-24 Power transmission mechanism with linear and rotation movement conversion

Country Status (5)

Country Link
US (1) US7584737B2 (en)
EP (1) EP1821001B1 (en)
JP (1) JP4647664B2 (en)
CN (1) CN100429431C (en)
WO (1) WO2006056126A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI495784B (en) * 2011-09-29 2015-08-11 Hon Hai Prec Ind Co Ltd Cylinder

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7360521B2 (en) * 2005-10-07 2008-04-22 Wavetech Engines, Inc. Reciprocating engines
FR2928693A1 (en) * 2008-03-17 2009-09-18 Antar Daouk Internal combustion engine
WO2010118518A1 (en) * 2009-04-16 2010-10-21 Korona Group Ltd. Rotary machine with roller controlled vanes
CN102102747A (en) * 2009-11-12 2011-06-22 蔡力兵 Latest technology for mutual conversion of reciprocating linear motoricity and continuous rotating force
CN101975119A (en) * 2010-09-18 2011-02-16 中国兵器工业集团第七○研究所 Novel internal-combustion engine
US8690245B2 (en) * 2010-11-18 2014-04-08 Wonderland Nurserygoods Company Limited Soothing apparatus and infant seat therewith
CN102135165B (en) * 2011-01-13 2013-04-24 深圳市晶金电子有限公司 Swing mechanism
CN102401153B (en) * 2011-07-05 2013-05-29 北京中电联环保工程有限公司 Rotary combined valve group and reactor applying same
US20130276761A1 (en) * 2012-04-24 2013-10-24 Patrick C. Ho Variable-compression engine assembly
JP5971721B2 (en) * 2012-11-05 2016-08-17 テクノダイナミックス株式会社 Cam device
ITVE20130020A1 (en) * 2013-04-22 2014-10-23 Pierfrancesco Poniz Motor not vibrating compact endothermic
CN103291872A (en) * 2013-06-21 2013-09-11 临沂奇润包装机械有限公司 Sine line speed change transmission mechanism
US9561595B1 (en) 2014-08-25 2017-02-07 Google Inc. Concentric opposed cam actuator
US9651133B2 (en) 2015-02-04 2017-05-16 Google Inc. Phased joint cam
CN105201644B (en) * 2015-08-01 2018-05-08 李长松 A kind of engine drive mechanism device
CN106948935A (en) * 2017-03-23 2017-07-14 大连理工大学 A kind of cylindrical cam rotor internal combustion engine dynamical system
CN110000125A (en) * 2019-04-19 2019-07-12 国网山东省电力公司建设公司 A kind of construction line of ink marker remove device

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2481363A1 (en) * 1980-04-27 1981-10-30 Inst Nat Motoare Termice divided combustion chamber
JPH0510148A (en) * 1991-06-29 1993-01-19 Mazda Motor Corp Structure of combustion chamber for engine
CN1081231A (en) * 1992-07-14 1994-01-26 黄强科 Synchronous internal combustion engine
CN1082141A (en) * 1993-05-07 1994-02-16 马育宁 Piston-rotating volume-varying mechanism
US5335634A (en) * 1991-05-14 1994-08-09 Mazda Motor Corporation Combustion chamber structure for an engine
DE19603119A1 (en) * 1995-01-30 1996-08-01 Aisin Seiki Combustion chamber for diesel engine with indirect injection
US6349694B1 (en) * 1998-06-26 2002-02-26 Alan Roger Babington Reciprocating mechanism and engine including the same

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2274097A (en) * 1938-10-27 1942-02-24 John B Sheerer Crankless engine
FR1333184A (en) * 1962-06-13 1963-07-26 Berliet Automobiles Development for internal combustion engines barrel
JPS55142901A (en) * 1979-04-03 1980-11-07 Takashi Uesugi Piston engine b
DE3224482C2 (en) * 1981-09-23 1991-11-21 Prodromos Bekiaroglou piston engine
JPH0219858U (en) * 1988-07-25 1990-02-09
JP3106171B2 (en) * 1989-07-15 2000-11-06 弘正 北口 Crankless engine mechanism
JPH062566A (en) * 1992-06-15 1994-01-11 T I Ii:Kk Power transmitting device
CN1096851A (en) 1994-01-28 1994-12-28 武守仁 Cam-type piston internal-combustion engine
US5566578A (en) * 1995-05-19 1996-10-22 Robert Sternoff Power recieving torque translating output device
US6250264B1 (en) * 1998-04-22 2001-06-26 Sinus Holding As Internal combustion engine with arrangement for adjusting the compression ratio
EP1179117A1 (en) * 1999-05-10 2002-02-13 Triune (Australia) Pty. Ltd. Drive mechanism and rotary displacer for hot air engines
AUPR462501A0 (en) * 2001-04-27 2001-05-24 Maslen, Des Radial engine
EP1474594B1 (en) * 2001-12-18 2012-08-15 Mechanical Innovation, Inc. Internal combustion engine using opposed pistons
US6988470B2 (en) * 2002-12-18 2006-01-24 Bruckmueller Helmut Swash plate combustion engine and method
US7360521B2 (en) * 2005-10-07 2008-04-22 Wavetech Engines, Inc. Reciprocating engines

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2481363A1 (en) * 1980-04-27 1981-10-30 Inst Nat Motoare Termice divided combustion chamber
US5335634A (en) * 1991-05-14 1994-08-09 Mazda Motor Corporation Combustion chamber structure for an engine
JPH0510148A (en) * 1991-06-29 1993-01-19 Mazda Motor Corp Structure of combustion chamber for engine
CN1081231A (en) * 1992-07-14 1994-01-26 黄强科 Synchronous internal combustion engine
CN1082141A (en) * 1993-05-07 1994-02-16 马育宁 Piston-rotating volume-varying mechanism
DE19603119A1 (en) * 1995-01-30 1996-08-01 Aisin Seiki Combustion chamber for diesel engine with indirect injection
US6349694B1 (en) * 1998-06-26 2002-02-26 Alan Roger Babington Reciprocating mechanism and engine including the same

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI495784B (en) * 2011-09-29 2015-08-11 Hon Hai Prec Ind Co Ltd Cylinder

Also Published As

Publication number Publication date
CN1779297A (en) 2006-05-31
US7584737B2 (en) 2009-09-08
JP4647664B2 (en) 2011-03-09
EP1821001A4 (en) 2010-09-01
JP2008520878A (en) 2008-06-19
EP1821001A1 (en) 2007-08-22
US20070295300A1 (en) 2007-12-27
WO2006056126A1 (en) 2006-06-01
EP1821001B1 (en) 2013-02-27

Similar Documents

Publication Publication Date Title
US8276552B2 (en) Opposed piston engine
US7194989B2 (en) Energy efficient clean burning two-stroke internal combustion engine
US7360511B2 (en) Opposed piston engine
US4174684A (en) Variable stroke internal combustion engine
RU2161712C2 (en) Internal combustion engine with opposed pistons
JP3943078B2 (en) Piston reciprocating engine with rotary cylinder
US4459945A (en) Cam controlled reciprocating piston device
CN100504050C (en) Rotary mechanism, machine comprising same or also including balancing mechanism
US4334506A (en) Reciprocating rotary engine
US20150114352A1 (en) Torque multiplier engines
US5375567A (en) Adiabatic, two-stroke cycle engine
US8210151B2 (en) Volume expansion rotary piston machine
EP1404946B1 (en) Radial internal combustion engine with floating balanced piston
EP0357291B1 (en) Crankless reciprocating machine
US4463710A (en) Engine connecting rod and piston assembly
US4509474A (en) Piston machine
US5546897A (en) Internal combustion engine with stroke specialized cylinders
US5535715A (en) Geared reciprocating piston engine with spherical rotary valve
US5623894A (en) Dual compression and dual expansion engine
US20090020958A1 (en) Methods and apparatus for operating an internal combustion engine
US4004421A (en) Fluid engine
EP1821001B1 (en) A power transmitting mechanism for the conversion between linear movement and rotary motion
KR100490247B1 (en) Improvements in axial piston rotary engines
CN101979853B (en) Internal dual-phase shockwave swing link transmission type internal combustion engine
US7980208B2 (en) Reciprocating engine

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
GR01 Patent grant
C14 Grant of patent or utility model